US4382476A - Manual torque magnifying impact tool - Google Patents
Manual torque magnifying impact tool Download PDFInfo
- Publication number
- US4382476A US4382476A US06/327,024 US32702481A US4382476A US 4382476 A US4382476 A US 4382476A US 32702481 A US32702481 A US 32702481A US 4382476 A US4382476 A US 4382476A
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- United States
- Prior art keywords
- handle
- axis
- inertia member
- tool head
- spring
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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- 230000002093 peripheral effect Effects 0.000 claims description 5
- 238000010276 construction Methods 0.000 abstract description 26
- 230000035939 shock Effects 0.000 abstract description 10
- 238000013461 design Methods 0.000 description 17
- 238000004519 manufacturing process Methods 0.000 description 8
- 229910000831 Steel Inorganic materials 0.000 description 5
- 239000010959 steel Substances 0.000 description 5
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- 230000006837 decompression Effects 0.000 description 2
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- 238000004146 energy storage Methods 0.000 description 2
- 239000007787 solid Substances 0.000 description 2
- 229910000851 Alloy steel Inorganic materials 0.000 description 1
- 208000013641 Cerebrofacial arteriovenous metameric syndrome Diseases 0.000 description 1
- 239000006096 absorbing agent Substances 0.000 description 1
- 230000003466 anti-cipated effect Effects 0.000 description 1
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- 238000000429 assembly Methods 0.000 description 1
- 239000000969 carrier Substances 0.000 description 1
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- 238000005336 cracking Methods 0.000 description 1
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- 238000011056 performance test Methods 0.000 description 1
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- 239000013585 weight reducing agent Substances 0.000 description 1
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
- B25B19/00—Impact wrenches or screwdrivers
Definitions
- the invention provides improvements to manually operated torque magnifying impact tools consisting of an improved inertia member construction affording a larger and continuous bearing surface, reduction in weight, and reduction of cost of manufacture; separate cams for disengaging each pawl to reduce cost of manufacture and maintenance of the tool; an improved tool head with a separable and replaceable drive bar for economy of manufacture and maintenance of the tool, and with a lesser number of teeth on the ratchet for improved performance of the tool and lesser force requirement on the handle to produce a given magnitude of torque output than with the tool of the said patents; improved means for stopping the inertia member including use of the pawls as stop members on the inertia member; addition of a spring stop member to limit the decompressive movement of the power spring and to absorb the shock associated with such movement; use of the power spring also as a recoil spring to stop the inertia member resiliently to reduce stress on tool parts; means to accomplish a more uniform input force requirement on the tool handle throughout its range of angular movement about the tool head
- FIG. 4 is a cross sectional view taken along the line 4--4 of FIG. 2;
- FIG. 5 is another detailed view of a portion of the device shown in FIG. 2;
- FIG. 7 is a detailed cross sectional view taken along the line 7--7 of FIG. 2;
- FIGS. 11 to 18 illustrate an alternative construction having a double handle wherein FIG. 11 is a plan view
- FIG. 12 is an elevational view with parts broken away
- FIG. 14 is a sectional view taken along the line 14--14 of FIG. 12;
- FIG. 15 is a sectional view taken along the line 15--15 of FIG. 12 with a spring 5 not shown;
- FIG. 16 is a sectional view taken along the line 16--16 of FIG. 12;
- FIG. 17 is a sectional view of a portion of FIG. 12;
- FIG. 18 is a sectional view of a portion of FIG. 12;
- FIG. 19 is a partial side sectional view of an alternative construction with a pivoted handle with cross slide 41 and spring 5, not shown, and
- FIG. 20 is an end view of FIG. 19.
- FIG. 19 can also be described as a vertical sectional view taken through the center of FIG. 20.
- the tool or tool assemblies of this invention comprise essentially a tool head 3 having a ratchet portion 6 with ratchet teeth 7 and a drive bar portion 10 extending axially on each end of the ratchet portion; an annular inertia member 4 surrounding the ratchet portion 6 on a common axis therewith; frame members 26 and 27 transverse the said axis at each end of the inertia member 4, respectively, and joined by cross members 32, cap screws 33 and nuts 34; a handle assembly 2 attached to each of frame members 26 and 27 extending perpendicularly to said axis; bearing means 28 and 12 attached to each of frame members 26 and 27 supporting inertia member 4 and ratchet portion 6, respectively, guiding the tool head 3, inertia member 4, frame members 26 and 27 and handle 2, for angular rotation relative to each other about said
- the theoretical degree of magnification of the torque value applied to the handle with respect to that delivered to the fastener being serviced is a function of the ratio that the magnitude of the angular movement of the handle bears to the corresponding angular movement of the drive bar resulting from the impacts of the pawls against the ratchet teeth.
- An important objective of this invention is to provide an improved inertia member construction for more economical manufacture and of lesser weight than that of the said patents.
- the inertia member be built up of laminates stamped from sheet metal or metal plate with the required pawl recesses and seats incorporated in the stamp configuration. This method is not completely satisfactory because the rivets used to join the laminates become loose as a result of repeated impacts on use of the tool, or by cracking of welds used as an alternative to the rivets to join the laminates.
- the pawl springs 25 are placed between the pawl and the inner surface 14 of the tube 13, with no requirement for machine work to form the pawl recess as required by the design of said patents.
- FIG. 8 An alternative configuration for the pawl seat 17 is indicated in FIG. 8 wherein the abutment 18 has a curved recess 72, preferably formed thereon prior to its attachment to the inertia member 4, to match the curved edge 22 of pawl 20, which recess, together with inner surface 14, forms the alternative pawl seat 73.
- FIG. 9 Another alternative configuration for construction of the pawl seat 17 and pawl retainer member 21 shown in FIG. 9, consists of a preformed pawl cage 19, combining the functions of pawl seat 17 and pawl retainer member 21, welded or otherwise suitably attached to tube 13.
- Various alternative constructions to serve the function of pawl seat 17 and pawl retainer 21 are readily apparent, so the constructions indicated by this invention are not limited to those described and shown.
- inertia member 4 slot 38 and pitman pin 39 are provided.
- an inertia member cam 67 is attached to the outer periphery of tube 13 as shown in FIG. 12 and described later herein.
- the pawl disengaging cam of the said patents consists of an integral member attached to the tool frame opposite the ends of the inertia member.
- This integral member includes a cam surface for each pawl, an interrupted bearing surface which mates with an inner bearing surface of the inertia member, and an inner bering surface supporting the integral round shaft extension of the tool head.
- This construction has several disadvantages, namely, it is expensive to manufacture, it provides an inadequate interrupted bearing surface to support the inertia member, and it is difficult to attach to the tool frame to prevent it from breaking loose as a result of shock load from the tool impacts.
- the improved pawl disengaging means of this invention consists of a separate cam for each pawl, such a cam 29 for each pawl being attached to frame member 26 and such a cam 29 for each pawl being attached to frame member 27.
- These cam units 29 carry only the load of disengaging the pawls, so thus are not subjected to any shock load resulting from the tool impacts as is the case with the combination cam and bearing design of the said patents.
- the cam 29 consists of a standard round head cap screw 30 whose shank passes through frame member 26 or 27 on which the particular cam is mounted and is secured on the opposite side by nut 31.
- the tool head of the said patents is an integral unit comprising a cylindrical portion with ratchet teeth on its periphery parallel to the axis of the cylinder, a round shaft extension axially at each end of the cylindrical portion, and a square shaft extending axially beyond the round shaft extension to engage the square opening of a standard socket for driving a nut or bolt head.
- Construction of the integral unit from solid steel stock reuires expensively machining away a substantial portion of the rough stock and also wasting a large amount of costly alloy steel.
- the square extension is vulnerable to breakage, being the weakest part of the unit, this breakage requires replacement of the entire expensive integral unit.
- this invention provides a tool head 3 with square drive bar 10 which is separable from a cylindrical ratchet portion 6.
- the ratchet portion 6 can be made from a short section of standard round steel bar with a minimum of machine work.
- a square opening 8 is cut axially through the ratchet portion 6 through which square drive bar 10, cut from standard square steel stock, is passed and held in place longitudinally by retaining tabs 11 welded to the bar 10 adjacent each end of the ratchet portion 6.
- a bearing surface 9 is machined at each end of the ratchet portion 6 and ratchet teeth 7 cut in its peripheral surface.
- opening 8 and drive bar 10 could be splined.
- This invention provides stop means on the inertia member and on the tool frame which not only serve the same purpose as the steps in patents Nos. 1 and 2, but which also eliminate the disadvantages associated with these stops described above for the tools of patents Nos. 1 and 2.
- These improved stop means include more than one stop member on the inertia member equally spaced about its axis, each such stop mating with a stop member attached to the frame member of the tool.
- FIGS. 2 and 6 One such arrangement is depicted in FIGS. 2 and 6 in which the ends of the pawls 20 extending between the ratchet 6 and the frame members 26 and 27 engage as stop members on the inertia member 4 with stop members 37, one stop 37 for each pawl, attached to each of frame members 26 and 27. Since these mating stop members are symmetrically arranged around the axis of the inertia member, their engagement imposes no load on the bearings 28 supporting the inertia member 4.
- FIG. 2 shows pitman assembly 40 including means for adjusting the distance between pin 39 and pin 46 as described earlier herein to readily provide said clearance at the desired value.
- Other means to adjust said clearance easily as may be required are readily apparent, and as stated earlier these adjusting means are not mandatory since the tool can be manufactured to operate satisfactorily without inclusion of the said adjusting means.
- Stop member 42 also serves an additional advantageous function by absorbing energy associated with stopping spring 5 following an impact of the tool in which all of the kinetic energy of rotation of the inertia member was not absorbed as impact on the tool head, thus relieving pitman 40 of the stresses associated with such an occurrence.
- a resilient cushion member 47 and back up plate 48 are provided between spring 5 and cross slide 41.
- Handle stop pin 53 is attached to handle flanges 50 which are joined to handle tube 49 by cross slide stop 42 and handle flange cover 51, said stop pin 53 is operable reciprocatingly in stop slot 56 on support members 54 to limit the range of said counterclockwise rotation of handle 2 on pin 52 after forcible engagement of pawls 20 with stops 37 subsequent to an impact of the tool in which all of the kinetic energy of rotation of the inertia member 4 was not absorbed as impact on tool head 3.
- FIG. 19 and FIG. 20 An alternative construction to that described in the immediately preceding paragraph to join handle 2 to frame members 26 and 27 to allow said limited counterclockwise rotation of the handle 2 relative to frame members 26 and 27 about a pivot to cause partial compression of spring 5 is shown in FIG. 19 and FIG. 20.
- cross slide stop 42 on handle tube 49 is extended perpendicularly to handle tube 49 to rest against an abutment 74 on each of crossmembers 32 to carry the thrust of spring 5 when the tool is at rest.
- Construction of the pivotal handle connection is not limited to those described herein, since other suitable constructions to provide the functions described are readily apparent.
- FIGS. 11 through 18 show another configuration of a tool using the spring 5 to serve both as a power spring and as a recoil spring in which two opposing handles 2, each enclosing a spring 5, with a handle boss 64 on each side of the handle tube 63 at one end and each boss seated in handle boss seat 66 on frame members 26 and 27 and secured to said frame members by cap screws 65 to fix handle 2 rigidly to frame members 26 and 27 with end closure plate 71 closing the space between handle and frame members, and in which pitman 40 and cross slide 41 of the tool of FIGS.
- means for compressing and decompressing spring 5 comprising an inertia member cam 67 attached to and extending circumferentially partially around and radially outward from the peripheral surface of inertia member 4, which cam includes a detent portion 68 with a power portion 69 and a recoil portion 70 circumferentially on opposite sides of detent portion 68, and a cam follower roller 57 mounted for rotation on roller pin 58 on support member 59 carried on a pivot pin 60 operable in bearing 61 on each of frame members 26 and 27, with support member 59 connected for operational contact with spring 5 by clevis 62.
- spring 5 comprising an inertia member cam 67 attached to and extending circumferentially partially around and radially outward from the peripheral surface of inertia member 4, which cam includes a detent portion 68 with a power portion 69 and a recoil portion 70 circumferentially on opposite sides of detent portion 68, and a cam follower roller 57 mounted for rotation on roller pin 58
- the pawl cams 29 disengage the pawls 20 from the ratchet teeth 7, whereupon the roller 57 recedes along power portion 69 toward the detent portion 68, meanwhile decompressing springs 5 and impelling the inertia member 4 to the position of reengagement of the pawls 20 with the respective successive ratchet teeth 7 to produce impact on the tool head 3.
- the inertia member and tool head will continue to rotate in a clockwise direction relative to handles 2 and cause the roller 57 to pass the detent portion 68 and move along the recoil portion 70 to partially compress springs 5 and thus absorb kinetic energy of rotation from the inertia member 4 not expended against the tool head 3 to contribute to bringing the inertia member 4 to a resilient stop, whereupon the roller 57 recedes to its rest position in detent portion 68.
- the cam-actuated spring compression means of the tool of FIGS. 11 through 18 has important advantages over the pitman-actuated spring compression means of the tool of FIGS. 1-10, namely, that the cam follower roller 57 operates with considerably less friction loss than does the cross slide 41, the inertia member 4 is stopped with less shock than that associated with the engagement of stop members 20 with stop members 37, and the contour of the power portion 69 of the inertia member cam 67 can be shaped so as to more adequately compensate for increasing pressure of the spring 5 during its compression to accomplish more uniform force requirement on the handle over its range of movement, and to reduce the force of the pawls on the ratchet teeth at the moment of their disengagement from the ratchet teeth to a lower value, than is possible with the pitman-actuated spring compression means of the tool of FIGS. 1-10.
- FIGS. 1-10 show a single handle tool with a pitman 40 and cross slide 41 coupling the inertia member 4 with spring 5, as indicated by the solid lines at the right side of the drawing, and a double handle tool created by addition of a second handle as indicated by combining the dotted lines at the left side of the drawing with the solid lines at the right side of the drawing.
- FIGS. 11-18 indicate a double handle tool in which the coupling means between the inertia member 4 and the springs 5 includes an inertia member cam 67 to actuate the springs 5, instead of pitman 40 and cross slide 41 as shown in the tool of FIGS. 1-10.
- the double handle tool is generally advantageous over the single handle tool because pure torque is applied to the handles by the operator, which is particularly desirable when using a drive extension between the tool and the work being serviced, and because, in contrast to the single handle tool, the force of the opposing springs against the inertia member is balanced, thereby minimizing the load on the inertia member bearings and the friction associated therewith, resulting in more efficient conversion of input torque to output torque than with the single handle tool.
- This reduced friction on the inertia member bearing has a further advantage for the double handle tool in that it permits providing for disengagement of the pawls at an angular position of the inertia member relative to the direction of force of the spring against this member which is closer in this respect to the dead center position of the inertia member without its locking to preclude decompression of the spring on such disengagement than is possible with the single handle tool with higher inertia bearing friction.
- the force of the pawls against the ratchet teeth at the moment of disengagement can be desirably minimized in the double handle tool, since this force approaches zero as the said angular position of the inertia member approaches zero.
- the cam-actuated spring design of FIGS. 11-18 is not well suited for a single handle tool because space limitations for the inertia member cam dictate use of a relatively short stroke for compression of the springs 5, which in turn requires high spring pressures against the inertia member to obtain the required amount of energy storage in the springs, with correspondingly high unbalanced load on the inertia member bearings in a single handle tool. Since the spring pressure on the inertia member by the opposing springs is balanced in the double handle tool, the high spring pressure associated with the cam-actuated spring design is not a significant detriment in the double handle tool design. The longer stroke for compression of the springs 5 in the design of FIG. 1 using pitman 40 and cross slide 41 for spring compression, and the associated lower unbalanced spring pressure against the inertia member bearings required to develop the amount of energy storage desired in the spring, renders this design suitable for construction in either the single handle or double handle configuration.
- Comparative performance tests indicate a weight reduction of over fifteen percent and a reduction in manual force requirement on the input handle of the tool of over twenty percent, for the same magnitude of torque output, for the tools constructed according to this invention, as compared to tools constructed in accordance with the said patents.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)
Abstract
Description
Claims (10)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US06/327,024 US4382476A (en) | 1981-12-03 | 1981-12-03 | Manual torque magnifying impact tool |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US06/327,024 US4382476A (en) | 1981-12-03 | 1981-12-03 | Manual torque magnifying impact tool |
Publications (1)
Publication Number | Publication Date |
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US4382476A true US4382476A (en) | 1983-05-10 |
Family
ID=23274806
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Application Number | Title | Priority Date | Filing Date |
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US06/327,024 Expired - Lifetime US4382476A (en) | 1981-12-03 | 1981-12-03 | Manual torque magnifying impact tool |
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US (1) | US4382476A (en) |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4919022A (en) * | 1988-04-29 | 1990-04-24 | Ingersoll-Rand Company | Ratchet wrench |
USRE33711E (en) * | 1985-05-15 | 1991-10-08 | Ingersoll-Rand Company | Ratchet wrench |
US5983757A (en) * | 1997-06-02 | 1999-11-16 | Snap-On Technologies, Inc. | Ratchet mechanism with laminated parts and method of making same |
US20060174467A1 (en) * | 2005-01-18 | 2006-08-10 | Rastegar Jahangir S | Manually operated impact tool |
US20060243108A1 (en) * | 2003-04-25 | 2006-11-02 | Precimed Sa | Detachable surgical ratchet |
US7258048B2 (en) * | 2005-04-16 | 2007-08-21 | Omnitek Partners L.L.C. | Manually operated impact wrench |
US11440169B2 (en) * | 2017-10-27 | 2022-09-13 | Gauthier Biomedical, Inc. | Torque limiting ratchet wrench |
Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2661647A (en) * | 1950-07-11 | 1953-12-08 | Oscar J Swenson | Ratchet type impact tool |
US2844982A (en) * | 1956-06-21 | 1958-07-29 | Oscar J Swenson | Ratchet-type, manually actuated, rotary impact tool |
US2954714A (en) * | 1958-11-12 | 1960-10-04 | Oscar J Swenson | Manually actuated rotary impact tool |
US3108506A (en) * | 1960-10-21 | 1963-10-29 | Oscar J Swenson | Rotary impact tools |
US3156309A (en) * | 1960-12-12 | 1964-11-10 | Oscar J Swenson | Rotary impact tools |
US3180185A (en) * | 1961-07-06 | 1965-04-27 | Curtiss Wright Corp | Accessory or adjunct for manual impact wrenches |
US3184998A (en) * | 1963-07-15 | 1965-05-25 | Curtiss Wright Corp | Impact wrench with stabilizer handle |
US4184552A (en) * | 1977-05-17 | 1980-01-22 | Marquette Metal Products Company | Manually actuated impact tool |
US4293044A (en) * | 1979-12-05 | 1981-10-06 | Marquette Metal Products Co. | Manually-actuated rotary-impact tool |
-
1981
- 1981-12-03 US US06/327,024 patent/US4382476A/en not_active Expired - Lifetime
Patent Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2661647A (en) * | 1950-07-11 | 1953-12-08 | Oscar J Swenson | Ratchet type impact tool |
US2844982A (en) * | 1956-06-21 | 1958-07-29 | Oscar J Swenson | Ratchet-type, manually actuated, rotary impact tool |
US2954714A (en) * | 1958-11-12 | 1960-10-04 | Oscar J Swenson | Manually actuated rotary impact tool |
US3108506A (en) * | 1960-10-21 | 1963-10-29 | Oscar J Swenson | Rotary impact tools |
US3156309A (en) * | 1960-12-12 | 1964-11-10 | Oscar J Swenson | Rotary impact tools |
US3180185A (en) * | 1961-07-06 | 1965-04-27 | Curtiss Wright Corp | Accessory or adjunct for manual impact wrenches |
US3184998A (en) * | 1963-07-15 | 1965-05-25 | Curtiss Wright Corp | Impact wrench with stabilizer handle |
US4184552A (en) * | 1977-05-17 | 1980-01-22 | Marquette Metal Products Company | Manually actuated impact tool |
US4293044A (en) * | 1979-12-05 | 1981-10-06 | Marquette Metal Products Co. | Manually-actuated rotary-impact tool |
Cited By (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
USRE33711E (en) * | 1985-05-15 | 1991-10-08 | Ingersoll-Rand Company | Ratchet wrench |
US4919022A (en) * | 1988-04-29 | 1990-04-24 | Ingersoll-Rand Company | Ratchet wrench |
US5983757A (en) * | 1997-06-02 | 1999-11-16 | Snap-On Technologies, Inc. | Ratchet mechanism with laminated parts and method of making same |
US20060243108A1 (en) * | 2003-04-25 | 2006-11-02 | Precimed Sa | Detachable surgical ratchet |
US7600451B2 (en) * | 2003-04-25 | 2009-10-13 | Greatbatch Medical Sa | Detachable surgical ratchet |
US20060174467A1 (en) * | 2005-01-18 | 2006-08-10 | Rastegar Jahangir S | Manually operated impact tool |
US7255029B2 (en) * | 2005-01-18 | 2007-08-14 | Omnitek Partners L.L.C. | Manually operated impact tool |
US7258048B2 (en) * | 2005-04-16 | 2007-08-21 | Omnitek Partners L.L.C. | Manually operated impact wrench |
US11440169B2 (en) * | 2017-10-27 | 2022-09-13 | Gauthier Biomedical, Inc. | Torque limiting ratchet wrench |
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